Balanced vane pump



Feb. 6, 1945. I I w TUCKER 2,368,789

- BALANCED VANE PUMP Filed 0qt. 21, 1941 5 Sheets-Sheet 1 Inventor WARREN RTuugEn re, 1945. WRT CKER 2,36 78 BALANCED VANE PUMP Filei Oct. 21, 19:11 I a Sheets-Sheet 3 JETS-.3

lnymior' v WARREN RTucKEKv auorncus Patented Feb. 6,1945

: UNITED STATES "PATENT OFFICE I 2,368,789 v r I I BALANCED VANE PUMP Warren R. Tucker, Dayton, Ohio, assignor to The Hydraulic Development Corp. Inc., wilming- I ton, Del.. a corporation of Delaware Application October 21, 1941, Serial No. 415,921

1 Claim.

within the pump causing an unbalanced condition upon the bearing 'supporting the working structure. .The' pressure developed within the pumps acts upon the surfaces of the pump ex posed to the pressure to cause a. resultant of force which is transverse'to the axis of rotation of the pump so that one side of the bearing supporting the rotating elements of .the pump carries a greater load. 1"

Itis an object of this invention to'provide a pump of the rotary type wherein the forces acting upon the rotating elements of the pump are balanced so that the load carried by the bearings of the pump is evenly distributed-over the entire surface of the bearings.

It is another object of the invention to pro vide a pump of the type having a rotating pumpeccentric manner with respect to the cylinder which is constructed and arranged in a manner ment.

Itis another object of the invention to provide av rotary pump wherein there is provided a plurality of rotating pumping elements which are arranged with respect to one another in a manner that the forces developed within the refrom the eccentric position of the central pumpvide a liquid pump of the rotary type having a plurality of pumping elements which are constructed and arranged for positive displacement of liquid and are positioned with respect to one another in a manner to balance the forces acting transversely of the pumping elements to eliminate unbalance of load'upon the bearings of the pump" structure.

It is a more specific object of the invention to] provide a liquid pump having a plurality of rotary pumping elements wherein the pumping elements are arranged in substantial axial alignment and the pumping elements adjacent opposite ends of the central pumping element are *of less volumetric capacit than. the centralpump ing element and are disposed eccentrically 180 'ing element whereby the transversely acting forces developed within the pumps are balanced. It is another object of the invention to provide a variable delivery fluid. pump constructed and ingelement operating within a cylinder in an arranged in accordance with the foregoing ob- .lects. I It is'another object of the invention to provide a fluid pump of. the vane type constructed and arranged in accordance with the foregoing ob- It is still another object of the invention to I provide a pump structure to produce the results spective-pumpsacting transversely to the axis of rotation of the pumps balance one another to evenly distribute the of'the pump.

Another object of the invention is to provide a fluid pump having a plurality of rotary pumping element which are disposed upon a common drive shaft in a manner that the transversely acting forces developed within the pumps balance each other to prevent unbalance ofload load upon the bearings upon the bearings for the drive shaft.

It is another object of the invention to provide a fluid pump having a plurality of rotary pumping elements which are secured together for concomitant rotation, and are arranged with respect to one another in a manner that the transversely acting forces developedby the pumping action set forth in the foregoing objects. I

Furtherobjects and advantages will become apparent from the following description and the drawings.

In the drawings: r Figure 1 is aside elevational'view of a pump constructed and arranged in accordance with the teachings of this invention.

Figure 2 ha horizontal cross-sectional view taken along iine-2-2 of Figure 1.

Figure 3 is a vertical cross-sectional view taken along line 3-3 of Figure l.

Figure 4 is a schematic cross-sectional view of the pumping elements of the pump of this in- 'v ention showing the relative positions of the pumping elements with respect to one another and the direction and magnitude of the forces developed withinthe pump to show the manner in which the forces balance each other.

of the respective pumping element balance each other.

It is another object of the invention to pro- Figure 5 is a view similar to Figure 4 but shows the pumping elements in a slightly diflerent po-.

sition from that shown in e 4 to indicate the manner in which the forces developed within the pump can shift and still maintain their balanced condition;

In this invention the pump is particularly '2l extends.

tween the drive shaft 2| and the opening 28- in the closure plate 23. The closure plate 24 is provided with an insert 36 threadedly engag ing the plate 24 to permit removal thereof gin.

rotary pumps wherein a rotor member is rotationally driven within a cylinder in a' manner that liquid is drawn into the cylinder upon one side thereof and is discharged throughv a port which is remote from the port of intake. When speaking of rotary type pumps, it is to be understood that such language includes pumps of the vane type, that is, those pumps having a rotating element within a cylinder which carries a plurality of radiallyextending vanes for engaging-the cylinder wall as .well as that type of pump which can be considered a truly rotary pump wherein the rotor itself engages the cylinder I wall.

This invention is also applicable to a radial type pump since a plurality of groups of cylinders can be arranged with respect to one another in a manner that the forces developed withinthe cylinders can oppose one another. I

The principles of this invention are particularly disclosed and described in connection with a vane type rotary pump. However, the principles oi the invention are not so limited and the disclosure only shows one form of a pump wherein the principles of the invention can be applied. V I

The pump it consists of a'casing it which is This is particularly true of composite rotor constructed and arranged to cooperate with a plurality of cylinders 31; 38

and 3t.

' rotor 25.

tegral annular ring 55 which extends through substantially Ll-shaped and having end walls l2 and is thereby providing a hollow interior it. A bottom wall or closure plate 95 is secured to the casing H by means of suitable bolts 56.

The end walls i2 and is are provided with openings W and i8 respectively for receiving bearings 99 and 29 respectively. The bearings is and is support the rotor 25 which will be hereinafter more specifically described. The

rotor 25 has a drive shaft 2!, extending from one end' thereof which is iournal'ed within the bearing i9 and has a bearing portion 22 upon.

the opposite end thereof which is lourn'aled in the bearing 29. As shown in the drawings, the

bearings 19 and 2b are of the ball type. However, the specific structure of the hearing may be considerably altered and it is these hearings which are to. be protected by the balancing of the forces within the pump.

End closure plates 23 and 2d are provided for the openings IT and I 8 respectively and are secured to the casing II by means or the bolts 26 and 21. The closure plate 23 is provided with Referring to Figure 3, each of the cylinders 37, 38 and 39 are substantially rectangularvin contour and have parallel walls and ti which slidably engage parallel walls 52 and d3-respectively of the casing in, the walls .42 and 63 being provided upon the wall surface of the interior it. The cylinders 8'5, 38 and 89 are provided with suitable bores 44. and 46 respectively within which the vanes 36, 33 and 38 respectively are adapted to be rotated'by meansof the The rotor 25 is a composite structure composed of a cylindrical flange as having a cylindrical ring 48 of smaller diameter as an integral part thereof whereby a shoulder 49 is provided for engaging the face 50 of one side of the cylinder 39. The cylindrical or annular ring %8 extends through the bore 46 of the cylinder 5% and has a cylindrical flange 5i secured thereto by means of a, plurality of bolts 52, thereby providing a shoulder 53 which engages the face 55 of the cylinder'ds. The flange 6i carries an inthe cylinder 38. The shoulder 56 engages the face 51 of the cylinder 38 while theshoulder 58 cylinder 37 and engages the annular ring 59 to all.

provide a shoulder tt which engages the face 64 of the cylinder 3'3. The annular ring 82 is provided with an annular flange toproduce a shoulder at which engages the face 6? of the cylinder 3% The annulargring 52 is secured to the annular ring-59 by means of a plurality of bolts 68. These various elementsheretofore de: scribed are thus associated with respect to one another to produce, a compositerotor which cooperates with the cylinders 87, 38 and 39 to provide the plurality of pumping elements at, 32 and 33. I

The annular rings d5, 5E and d2 of the rotor 25 are provided with slots within which the vanes 3t, 35 and as respectively are slidably carried.

an opening 28 through which the drive shaft A suitable seal 29 is provided hemetric capacity which is double that of either of the pumping units 3 1 01- 3| so that the force developed withinthe pumping unit 32 will be dou ble that developed within either of the pumping units or 33. Each of the pumping elements v 1. 3|, 32 and 33 is provided with a pluralityoiv vanes 84, 35 and positioned as shown in Figure As shown in Figure 3, the slots at extend through th annular rings l8, l5 and 62 so that the outer ends of the vanes carried therein engage the bores it, 85 and 4d of the respective cylinders.

The inner ends of the vanes 2d, 85 and 36 extend within the cylindrical bores 10,. and it of the annular rings 62, 55 and 48 respectively. The inner ends of the vanes 34, 35 and 38 engage the surface of conical shaped plugs 13, I4 and 75, the

' inner edges of the vanes being provided with an 34. 35 and 38 with 44, 45 and it.

angular surface to cooperate with the surfaces of the plugs. The plugs I3, I4 and I5 thus provide means for insuring engagement of the vanes their respective cylinder walls To insure engagement of thesurfacesof the plugs 13, "and 18 with the respective cooperating vanes, a plurality of springs is provided for urging the plugs in a direction to continuously urge the vanes in an outward direction. A spring 16 is positioned within the bore 11 provided in one end of the rotor 28, one "endof the spring 16 engaging an adjusting screw 18 which threadedly engages the bore 11 while the opposite end k asoarec of the spring engages a friction button 18 which in turn engages the actuator plug 13 for urging the same in a rightward direction as viewed in Figure 2.

A spring 80 ispositioned between the actuator plugs 18 and I4 and has the opposite ends thereof engaging the friction buttons 8| and 82 which in turn engage the plugs II and ll-respectively. The spring 80 has less expansive force than the spring 18 andv therefore will not effect the action of the spring 16 upon the plug 13. The spring 80 however does urge the actuator plug it in a rightward direction. A similar spring assembly 83 is provided between the actuator plugs 16 and 15 for urging the plug 15 in a rightward direction.

A spring 84 is positioned within a bore 85 pro vided in the drive shaft end of the rotor 25 for posite end of the lever is provided with a yoke which engages a reduced diameter portion -I provided on the stem 88. The lever I02 is prosure upon the spring 16 occasioned by the moos slty of a repair operation to the pump.

The fluid or liquid pump it is of the variable delivery type wherein the rotor of the pump is mounted upon a permanent axis for rotation therein; while the cylinders cooperating with the rotors are movable with respect to the axis of the rotor to change the eccentricity between the rotor and the cylinder, and thereby vary the volume of fluid discharged from the pump. The cylinders 81, 88 and 89 are slidably mounted in the manner which has heretofore been described to permit movement thereof with respect to the rotor 25. The eccentric position of the cylinders 81 and 39 with respect to the rotor 25 is 180 opposite to the eccentric position of the cylinder 88; Therefore, the fluid inlet and discharge ports for the cylinders 31 and 39 will be 186 from the corresponding iiuid inlet and outlet for the cylinder 38. The purpose of this eccentric arrangement 1 of the cylinders will be hereinafter more fully described.

To change the volume of nuid'discharged from the various cylinders the cylinders 31 and 39 must be moved in a direction opposlte'to that of the cylinder 38 since their eccentricities are 189 away from that of the cylinder 38.

The mechanism for controlling the volume of the flow of fluid from the pump 10 consists of a threaded stem 85 which is in threaded engagement with the casing ll having a threaded opening 81. The inner end of the stem 06 carries an enlarged head 88 which is retained within a recess 88 provided in the wall of the cylinder 38 by means of a plate 90 secured to the cylinder 08 by means of the bolts or screws 9!. The outer end of the stem 86 is provided with an operating wheel 92 for rotating thesteam within the threaded opening 81 and thus moving the cylinder 38 with respect to the rotor 25 to change theeccentricity therebetween.

The cylinders 31 and 3e are provided with actuating pins 93 and 93 respectively which are in slidabie engagement with the holes and 98" provided in the casing H. The inner ends of the pins 93 and 94 are provided with enlarged heads 91 and 98 which engage the cylinders. 31

and 39 and are retained in position in the samev manner as the head 38. The outer ends of the.

actuating pins 93 and it are provided withannular recessed portions 99 and I0!) respectively.

A pair of levers Hil and W2 is pivotally mounted I vided with a yoke "0 which engages the recess I00 of the actuating pin 84 and has ayoke 108a on the opposite end thereof similar to the yoke I08 of the lever l0l for engaging the recess I09. It may be seen from the drawings that when the stem 86 is moved in one direction or the other that the actuating pins 93 and 94 will move in a the change of eccentric position of the cylinder 38 with respect to the rotor 25.

Since the cylinders of the pump it are capable o! movement-with respect tothe rotor the volume of fluid discharged by the pump can be varied from a minimum to a maximum and by shifting the eccentricity oi the cylinders 180 with respect to the rotor the direction of flow of fluid through the pump can be changed.

The pump ill is provided with port passages which can he used either as inlet or discharge passages depending upon the eccentric position of the, cylinders with respect to the rotor 25. A

port passage ill in the base or closure member I5 communicates with a passage H2 provided in the cylinder 38. A similar port passage H3 in -the casing ii communicates with a-passage H4 provided in the cylinder 38, the passage H4 belng positionedl80 from the passage H2. 'These passages provide the fluid flow conduits through der bore thereof. The cylinders 31 and 39 have similar fluid flow passages. As seen in Fisure 1 the conduit H5 which connects with the port passage l l l' of the cylinder 38 also connects to the port passages ll! of the cylinders 31 and 89 but 18ll iroin the port passage iii. A com dult H6 connects with the port passage N3 of the cylinder 38 and also to the port passages Ill oi the cylinders 31! and 39. It may thus be seen that the discharge ports for the cylinders 31 and 39 are 180 from the discharge port for the cylinder 38.

A suitable motor in is connected to the drive shaft 2| oi the pump l0 for driving the same.

The pump as herein described is constructed and arranged to balance the transverse thrust thereof, which load upon the bearing occurs subiii) stantially opposite tothe discharge opening of the cylinder within which the rotor is operating. The-pressure within the compression chamber thus causes the development of a transverse force which normally in rotary fluid pumps cannot be ofiset when a single pumping chamber is utilized.

a In this invention there is provided three pump units each consisting o! a rotor and a cylinder, the rotors being of the same diameter and the cylinders being of equal diameter. Two of the rotors and cylinders have displacement areas which are half as wide as the third rotor. and

. cylinder so that the surface areas of the rotors of the two smaller pumping units will be equal to the surface area of the large pumping unit. The

small pumping units are positioned at opposite ends of the large pumping unit and since all of the cylinder 38 and communicate with .the cyllntransverse thrust transmitted to 4- I f I 2,368,789 I v, i

sure on the rotor being represented by the ar-' the rotors of the pumping-units are assembled into a composite structure, the forces developed "opposite ends of the large pumping unit, the

transverse forces developed by the units will balance each other so that the resultant force applied to the bearings supporting the rotor-is substantially a neutral force. r The analysis of the, forces developed within in Figures 4 and 5. In Figure 4 the arrows A indicate the direction of rotation of the three pump units. In this analysis diagram the pumping elements 3| and 33 have their discharge passages Htpositioned at the lower side of the pump so that the transverse force developed as a result of the compression of fluid passing through the pump is in the upward direction as indicated by thearrows B. The pumping element'32 is provided with its discharge passage H8 at the upper side of the unit so that the transverse force developed by the pumping unit 32 is in a downwarddirection as indicated-by the arrow C. As previously mentioned the diameter of th e cylinder bores for the pumping units 3!, 32 and 33 is equal as is the diameter of the rotors for these cylinders. However, the length of the rotor for the pumping unit 32 is twice the length of the rotors for the pumping units 3! and 33, hence the transverse force developed by the pumping unit 32 will be double the magnitude of theiorce developed by either of the pumping units 3! and 33. However, since the transverse forces developed by the pumping units 3i and 33 are applied to the composite rotor in a direction opposite to the transverse force of the pumping. unit 32 the resultant effect is to produce a condition of balanced forces so that there is no I the bearings which support the rotor.

In Figure there is shown the same type of diagram as shown in Figure 4 but having the vanes 01 the pumping units advanced slightly in their-rotative position with regard to them, let and outlet ports for the cylinders. It will V be noted that the position of the direction of the transverse forces developed within the pump have been changed slightly but these forces still apply themselves to the rotors in opposite and sub stantially parallel directions. The shift in the row B. The surfacearea of the rotor for the .pumping unit 32 which is exposed to the pressure in the pumping unit 32 is from the vanerection of the forces tends to shift slightly during rotation of the rotor that the forces win always maintain a balanced condition.

While in the description of this invention it has been specifically mentioned that the rotor of the pumping unit 32 is twice the width of the rotors for the pumping units stand 33 in order the diameters of the cylinder and rotors with the rotary pump is diagrammatically illustrated respect to one another and decreasing or increasing the respective lengths of the rotors to compensate for the difference indiameter's .of the cylinders, the necessary result being that the I claim as new and desire to secure by Letters Patent is? forces'is due to the fact that the surface area exposed to the pressure has shifted to'the left in the pumping units ti and 33 while the-surface area exposed to the pressure has shifted to the right in the pumping unit 32. In Figure 5 the surface area of the rotor of the pumping units 3! and 33 exposed to the pressure extends from the vane tea to the'vane 85b of the pumpingunit 8i and from the vane 36a to the vane 38 upon the pumping unit 38, the resultant pres- I A liquid pump of the vane type comprising a plurality of independent cylinders including a central cylinder and a cylinder adjacent each end of said central cylinder having an internal surface area less. than the internal surface area of said central cylinder, a rotor associated witheach of said cylinders, said rot'ors being secured spect to said rotors, said end cylinders having the compression chambers thereof disposed diametrically opposite to said central cylinder, said end cylinders having their compression chambers so proportioned to the compression chamber of.

said central cylinder that the transverse forces produced within said end cylinders upon, said rotor assembly'are substantially equal to each other and the combined forces are equal to the transverse 'forces produced within said central cylinder and applied uporrsaid rotor assembly 'in a diametrically opposed direction to thereby balance all forces upon said rotor assembly, and

means including means, connected withsaid 9C? centrically positioning means, for adjusting said end cylinders and said central cylinder in diametrically opposite directions for simultaneously changing the eccentricity of adjacent cylinders. with respect to said rotor in opposite directions-- said eccentric adjusting means further including an adjustable stem member engaging said central cylinder and adjustably engaging said casing, and

a pair of oppositely extending links attached at.

one of their-ends to'said stem member, the opp site ends of each of said links being conne t d to an end cylinder. v i w WARREN a. TUCKER. 

